CN103228871B - Turbine - Google Patents
Turbine Download PDFInfo
- Publication number
- CN103228871B CN103228871B CN201180056739.9A CN201180056739A CN103228871B CN 103228871 B CN103228871 B CN 103228871B CN 201180056739 A CN201180056739 A CN 201180056739A CN 103228871 B CN103228871 B CN 103228871B
- Authority
- CN
- China
- Prior art keywords
- stepped part
- blade
- whirlpool
- ladder surface
- towards
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 239000012530 fluid Substances 0.000 claims abstract description 28
- 238000007789 sealing Methods 0.000 claims description 45
- 238000011144 upstream manufacturing Methods 0.000 claims description 36
- 238000000926 separation method Methods 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 25
- 230000000630 rising effect Effects 0.000 description 17
- 239000002023 wood Substances 0.000 description 17
- 230000015572 biosynthetic process Effects 0.000 description 6
- 230000001681 protective effect Effects 0.000 description 5
- 230000003068 static effect Effects 0.000 description 5
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 4
- 230000001105 regulatory effect Effects 0.000 description 4
- 230000003321 amplification Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 229910052742 iron Inorganic materials 0.000 description 2
- 238000003199 nucleic acid amplification method Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 239000000126 substance Substances 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000002271 resection Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
- F01D11/04—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type using sealing fluid, e.g. steam
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
- F01D5/14—Form or construction
- F01D5/20—Specially-shaped blade tips to seal space between tips and stator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/08—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between rotor blade tips and stator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/08—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between rotor blade tips and stator
- F01D11/10—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between rotor blade tips and stator using sealing fluid, e.g. steam
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
- F01D5/22—Blade-to-blade connections, e.g. for damping vibrations
- F01D5/225—Blade-to-blade connections, e.g. for damping vibrations by shrouding
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/20—Three-dimensional
- F05D2250/29—Three-dimensional machined; miscellaneous
- F05D2250/294—Three-dimensional machined; miscellaneous grooved
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
Abstract
This turbine is provided with: a blade; a structure which is provided on the tip side of the blade with a clearance therebetween and rotates relatively to the blade; a step part which is provided at the tip of the blade, has at least one step surface, and protrudes toward a region facing the tip in the structure; a seal fin which is provided in the region facing the tip in the structure, extends to the step part, and forms a very small clearance between the step part and itself; and a cut part which is formed in the step surface so as to be continuous with the upper surface of the step part. The cut part guides a separation vortex separated from the mainstream of a fluid flowing through the clearance to the seal fin on the upper surface of the step part.
Description
Technical field
The present invention relates to the turbine that a kind of such as power station, chemical plant, gas plant, iron works, boats and ships etc. use.
The Patent 2010-286583 Patent Application claims preference that the application submitted in Japan on December 22nd, 2010, and its content is applied at herein.
Background technique
All the time, as the one of steam turbine, possess multistage housing, being rotatably located at the axis body (rotor) of enclosure interior, the stator blade of fixed configurations in the inner peripheral portion of housing and the downstream side at this stator blade, to be located at the steam turbine of the movable vane on axis body radially known.The pressure energy of steam is converted to kinetic energy by stator blade by the impact wheel in such steam turbine, by movable vane, this kinetic energy is converted to kinetic energy of rigid body (mechanical energy).In addition, pressure energy is also converted to kinetic energy by the reaction turbine in steam turbine in movable vane, and this kinetic energy is converted to kinetic energy of rigid body (mechanical energy) by the reaction force sprayed by steam.
In this steam turbine, between the front end of movable vane and the housing forming vapor flow path around movable vane, be usually formed with radial gap, and between the front end and axis body of stator blade, be also formed with radial gap.
But, turning power is not applied to movable vane to downstream side by the leaked steam in the gap of movable vane front end.In addition, by stator blade, pressure energy cannot be converted to kinetic energy to downstream side by the leaked steam of stator blade front end, therefore hardly turning power be applied to the movable vane in downstream side.Therefore, in order to improve the performance of steam turbine, the amount of the leaked steam in described gap is importantly reduced by.
At this, propose the structure (for example, referring to patent documentation 1) shown in Fig. 9.In the structure shown here, such as stepped part 502(502A that height uprises towards downstream side gradually from running shaft direction (hreinafter referred to as axis) upstream side, 502B, 502C is provided with at the front end 501 of movable vane 500).Be provided with relative to stepped part 502(502A, 502B, 502C at housing 503) there is sealing fin 504(504A, 504B, 504C of micro-gap H101, H102, H103).
By formation like this, through sealing fin 504(504A, 504B, 504C) the leak fluid of micro-gap H101, H102, H103 and stepped part 502(502A, 502B, 502C) formation ladder surface 506(506A, 506B, 506C) end edge portion (edge part) 505(505A, 505B, 505C) collide, thus flow resistance can be made to increase.In addition, at ladder surface 506(506A, 506B, 506C) end edge portion 505(505A, 505B, 505C) steam peeled off becomes and peels off whirlpool Y100.This stripping whirlpool Y100 produces from sealing fin 504(504A, 504B, 504C) front end towards the sinking of the front end 501 of movable vane 500.This sinking plays the contracted flow effect of the steam by micro-gap H101, H102, H103.Therefore, reduced by the flow of the leaked steam of micro-gap H101, H102, the H103 between housing 503 and the front end 501 of movable vane 500.
Prior art document
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Publication 2006-291967 publication
Summary of the invention
As shown in Figure 9, the closer to downstream side, less by the density of the fluid of movable vane 500, therefore the closer to downstream side, by stepped part 502(502A, 502B, 502C) the flow velocity of steam faster.That is, with regard at ladder surface 506(506A, 506B, 506C) end edge portion 505(505A, 505B, 505C) with regard to the steam peeled off, the steam in downstream side, radial velocity is larger.Therefore, when by ladder surface 506(506A, 506B, 506C) angle of inclination when being set as equal, formed the closer to downstream side more to the stripping whirlpool Y100 radially bent.With regard to the stripping whirlpool Y100 of this shape, contracted flow effect is little and the low effect of differential static pressure is also little, is therefore difficult to the leakage flow of the steam of micro-gap H101, H102, the H103 of the front end 501 being reduced by movable vane 500.
Therefore, the present invention completes in view of the above circumstances, provides a kind of high performance turbine being reduced by the leakage flow of the steam of the micro-gap of the front end of blade further.
Turbine of the present invention possesses blade and structure, this structure leaves gap and is arranged at the front end side of described blade, and relatively rotate relative to described blade, fluid circulates in described gap, in described turbine, any one party in the described front end of described blade and the described structure position relative with described front end is provided with stepped part, this stepped part at least has a ladder surface and outstanding to opposite side, sealing fin is provided with at described opposite side, sealing fin extends towards described stepped part, and micro-gap is formed between this stepped part, cut portion is provided with at described ladder surface, this cut portion is formed in the mode be connected with the upper surface of described stepped part, at this upper surface, the stripping whirlpool that the main flow from described fluid is peeled off is guided towards described sealing fin.
By formation like this, to collide with a part for the main flow of the fluid by blade and ladder surface and the mode returning upstream side forms main whirlpool, and to peel off the fluid of a part and the stripping whirlpool that formed to rotating with main whirlpool opposite direction from main whirlpool at the end edge portion (edge) of ladder surface.That is, peel off whirlpool to produce from sealing the sinking of fin front end towards stepped part.Therefore, peel off the contracted flow effect that the fluid by the micro-gap between sealing fin front end and stepped part is played in whirlpool, therefore, it is possible to reduce leakage flow.
At this, ladder surface forms cut portion in the mode be connected with the upper surface of stepped part.That is, the end edge portion of ladder surface cut portion excision, guides stripping whirlpool to sealing fin compared with end edge portion.Therefore, compared with not forming the situation of cut portion, in the reduced in the stripping whirlpool nearby formed of sealing fin.Therefore, the sinking grow produced by stripping whirlpool near sealing fin front end, thus the contracted flow effect of the fluid by gap can be improved further.
In addition, by reducing the diameter peeling off whirlpool, the static pressure of the upstream side of sealing fin can be made to reduce.Therefore, it is possible to make the differential pressure between upstream side and downstream side diminish across sealing fin.Therefore, it is possible to reduce leakage flow further.
Turbine of the present invention also can be, described stepped part has multiple described ladder surface, and formed in the mode that projecting height uprises from upstream side gradually towards downstream side, described cut portion is the rake being formed at each ladder surface and tilting towards described downstream side from described upstream side, and each rake is set as that relative to the angle of inclination of running shaft radial direction the described angle of inclination of the described rake formed at the described ladder surface in described downstream side is larger.
By formation like this, upstream side can both the make velocity vector in stripping whirlpool same with downstream side is towards sealing fin forward end (axis).Therefore, it is possible to make the diameter approximate equality in the stripping whirlpool formed in each stepped part.That is, even if the flow velocity of the fluid on each ladder surface of stepped part changes, the diameter in the stripping whirlpool formed at each ladder surface also can be made to reduce substantially uniformly.Therefore, it is possible to reliably improve the contracted flow effect produced by the stripping whirlpool of the fluid by micro-gap further, and reliably can reduce the static pressure of the upstream side of sealing fin further.
Turbine of the present invention also can be, described stepped part has multiple described ladder surface, and formed in the mode that projecting height uprises from upstream side gradually to downstream side, described cut portion has arcus part, this arcus part is formed at each ladder surface, and be connected with described upper surface smoothly from described upstream side towards described downstream side, the angular setting between the tangent direction at the position that described arcus part is connected with described upper surface and running shaft radial direction is that the described angle of the described arcus part formed at the described ladder surface in described downstream side is larger.
By formation like this, even if the flow velocity of the fluid on each ladder surface of step changes, the diameter in the stripping whirlpool formed at each ladder surface also can be made to reduce substantially uniformly.Therefore, it is possible to reliably improve the contracted flow effect produced by the stripping whirlpool of the fluid by micro-gap further, and reliably can reduce the static pressure of the upstream side of sealing fin further.
Invention effect
According to the present invention, compared with not forming the situation of cut portion, the reduced in the stripping whirlpool nearby formed at sealing fin can be made.Therefore, the sinking grow produced by stripping whirlpool near sealing fin front end, thus the contracted flow effect of the fluid by micro-gap can be improved.
In addition, by reducing the diameter peeling off whirlpool, the static pressure of the upstream side of sealing fin can be reduced.Therefore, it is possible to the differential pressure reduced between upstream side and downstream side across sealing fin.Therefore, it is possible to reduce leakage flow further.
Accompanying drawing explanation
Fig. 1 is the schematic configuration sectional view of the steam turbine represented in embodiments of the present invention.
Fig. 2 is the amplification sectional view of the significant points I represented in Fig. 1.
Fig. 3 is the Action Specification figure of the steam turbine in embodiments of the present invention, and (a) is the enlarged view of the significant points I in Fig. 1, and (b) is the significant points enlarged view of (a).
Fig. 4 is the schematic configuration sectional view of the stepped part in the first variation of the present invention.
Fig. 5 is the schematic configuration sectional view of the stepped part in the second variation of the present invention.
Fig. 6 is the schematic configuration sectional view of the stepped part in the 3rd variation of the present invention.
Fig. 7 is the schematic configuration sectional view of the stepped part in the 4th variation of the present invention.
Fig. 8 is the schematic configuration sectional view of the stepped part in the 5th variation of the present invention.
Fig. 9 is the summary construction diagram of the significant points in steam turbine in the past.
Embodiment
(steam turbine)
Then, based on Fig. 1 ~ Fig. 4, embodiments of the present invention are described.
Fig. 1 is the schematic configuration sectional view of the steam turbine representing embodiments of the present invention.
Steam turbine 1 is formed primarily of such as lower part: housing 10, adjustment flow into the amount of the steam S of housing 10 and pressure regulating valve 20, be rotatably arranged at housing 10 inner side and by transmission of power to the axis body 30 of the equipment such as not shown generator, the stator blade 40 being held in housing 10, the movable vane 50 be located on axis body 30, axis body 30 supported bearing portion 60 for pivoting.
Bearing portion 60 possesses journal bearing device 61 and thrust bearing device 62, supports axis body 30 into rotatable.
Housing 10 is streams of steam S.The inner space of housing 10 is hermetically sealed.The dividing plate foreign steamer 11 of the ring-type of inserting for axis body 30 is firmly fixed at the internal face of this housing 10.
Regulating valve 20 is installed multiple in the inside of housing 10.Each regulating valve 20 possesses adjustment valve chamber 21, spool 22 and the valve seat 23 that the never illustrated boiler of steam S flows into respectively.When spool 22 leaves from valve seat 23, vapor flow path is opened, thus steam S flows into the inner space of housing 10 via vaporium 24.
Multiple disks 32 that axis body 30 possesses axle main body 31, extends along running shaft radial direction (hreinafter referred to as radial direction) from the periphery of this axle main body 31.This axis body 30 transmits kinetic energy of rigid body to equipment such as not shown generators.
Stator blade 40 configures multiple radially in the mode around axis body 30 and is formed ring-type stator blade group.Each stator blade 40 is held in dividing plate foreign steamer 11 respectively.Inner side in the radial direction of these stator blades 40 is connected by the wheel hub protective cap 41 of ring-type.This wheel hub protective cap 41 has inserted axis body 30.The front end of stator blade 40 leaves radial gap relative to axis body 30 and configures.
The ring-type stator blade group be made up of these multiple stator blades 40 leaves interval vertically and forms six.The pressure energy of steam S is converted to kinetic energy and is guided to movable vane 50 side adjacent in downstream side by steam S by ring-type stator blade group.
Movable vane 50 is installed on the peripheral part of the disk 32 that axis body 30 has securely.This movable vane 50 passes through in the downstream side of each ring-type stator blade group configure multiple radially and form ring-type movable vane group.
These ring-type stator blade groups and ring-type movable vane consist of one group of one-level.Steam turbine 1 has six groups of ring-type stator blade groups and ring-type movable vane group.Blade tip guard shield 51 is circumferentially provided with at the front end of these movable vanes 50.
At this, in the present embodiment, axis body 30 and dividing plate foreign steamer 11 form " structure " in the present invention.In addition, stator blade 40, wheel hub protective cap 41, blade tip guard shield 51 and movable vane 50 form " blade " in the present invention.And when stator blade 40 and wheel hub protective cap 41 are " blades ", axis body 30 is " structures ".On the other hand, when movable vane 50 and blade tip guard shield 51 are " blades ", dividing plate foreign steamer 11 is " structures ".In addition, in the following description, be " structure " with dividing plate foreign steamer 11, be described for " blade " with movable vane 50.
Fig. 2 is the amplification sectional view of the significant points I represented in Fig. 1.
As shown in Figure 2, the blade tip guard shield 51 being located at the front end of movable vane 50 leaves gap K with the dividing plate foreign steamer 11 being fixed on housing 10 and relatively configures.Blade tip guard shield 51 possesses to the outstanding stepped part 52(52A ~ 52C in dividing plate foreign steamer 11 side).Each stepped part 52(52A ~ 52C) there is ladder surface 53(53A ~ 53C).
The blade tip guard shield 51 of present embodiment possesses three stepped part 52(52A ~ 52C).Upper surface 152(152A ~ the 152C of these three stepped part 52A ~ 52C) uprise gradually from the projecting height that movable vane 50 is outstanding along with the axial upstream side (left side Fig. 2) from axis body 30 tends to downstream side (right side in Fig. 2).Ladder surface 53(53A ~ the 53C of stepped part 52A ~ 52C) towards axial upstream side.
At this, each ladder surface 53(53A ~ 53C) form rake 56(56A ~ 56C to roll oblique mode to downstream respectively).That is, each ladder surface 53(53A ~ 53C) formed rake 56(56A ~ 56C by excising obliquely).And, rake 56(56A ~ 56C) rising wood 55(55A ~ 55C) with stepped part 52(52A ~ 52C) upper surface 152(152A ~ 152C) be connected.
In addition, rake 56(56A ~ 56C) to be set as more tending to downstream side relative to the tilt angle theta 1 ~ θ 3 of radial direction larger.That is, at three stepped part 52(52A ~ 52C) in will be defined as θ 1 relative to the angle of inclination of radial direction being positioned at the rake 56A that the ladder surface 53A of the first order stepped part 52A of side, most upstream is formed.θ 2 will be defined as being positioned at the rake 56B that the ladder surface 53B than the second level stepped part 52B of first order stepped part 52A downstream is formed relative to the angle of inclination of radial direction.θ 3 will be defined as being positioned at the rake 56C that the ladder surface 53C than the third level stepped part 52C of second level stepped part 52B downstream is formed relative to the angle of inclination of radial direction.
θ 1, θ 2 and θ 3 are set as meeting
θ3＞θ2＞θ1。
On the other hand, on dividing plate foreign steamer 11, be formed with annular slot 111 at the position that blade tip guard shield 51 is relative with stepped part 52.Annular slot 111 with three stepped part 52(52A ~ 52C) corresponding mode has the recess 111A ~ 111C of three ring-types expanding gradually from upstream side towards downstream side.In addition, annular slot 111 has and is formed at most downstream side and the diameter fourth stage recess 111D less than third level recess 111C.
At this, be positioned at first order recess 111A and second level recess 111B boundary end edge portion (edge part) 112A, be positioned at the boundary of second level recess 111B and third level recess 111C end edge portion 112B and be positioned at third level recess 111C and fourth stage recess 111D boundary end edge portion 112C on be provided with towards blade tip guard shield 51 and three that extend to radially inner side seal fin 15(15A ~ 15C).Sealing fin 15(15A ~ 15C) respectively with stepped part 52(52A ~ 52C) relative.
Each sealing fin 15(15A ~ 15C) at each self-corresponding stepped part 52(52A ~ 52C) between be radially formed with micro-gap H(H1 ~ H3).These micro-gaps H(H1 ~ H3) each size scope of safety that both can not contact on the basis considering the thermal expansion length of housing 10 and movable vane 50, the centrifugal elongation of movable vane 50 etc. in be set as minimum.
In addition, in the present embodiment, H1 ~ H3 is identical size.But, H1 ~ H3 can be changed as required and suitably.
On the basis of such structure, between blade tip guard shield 51 and dividing plate foreign steamer 11, at each stepped part 52(52A ~ 52C) and three recess 111A ~ 111C of the annular slot 111 corresponding with it between be formed with cavity C (C1 ~ C3).
More specifically, be formed at side, most upstream and first cavity C 1 corresponding with first order stepped part 52A between the inwall side 54A of the upstream side of sealing fin 15A corresponding to first order stepped part 52A and first order recess 111A, and to be formed between blade tip guard shield 51 and dividing plate foreign steamer 11.
And, second cavity C 2 corresponding with second level stepped part 52B the upstream side of sealing fin 15B corresponding to second level stepped part 52B and second level recess 111B inwall side 54B and be located at end edge portion 112A sealing fin 15A between, and to be formed between blade tip guard shield 51 and dividing plate foreign steamer 11.
And, three cavity C 3 corresponding with third level stepped part 52C sealing fin 15C corresponding to third level stepped part 52C and the internal face 54C in downstream side of third level recess 111C and the internal face 54D of the upstream side of third level recess 111C and be located at end edge portion 112B sealing fin 15B between, and to be formed between blade tip guard shield 51 and dividing plate foreign steamer 11.
(action of steam turbine)
Then, the action of steam turbine 1 is described based on Fig. 1 ~ Fig. 3.
Fig. 3 is the Action Specification figure of steam turbine, and (a) is the enlarged view of the significant points I in Fig. 1, and (b) is the significant points enlarged view of (a).
As shown in Fig. 1 ~ Fig. 3 (a), first, when making regulating valve 20 be in open state, the never illustrated boiler of steam S flows into the inner space of housing 10.
Flow into the steam S behind the inner space of housing 10 successively by the ring-type stator blade group at different levels and ring-type movable vane group.Now, by stator blade 40, pressure energy is converted to kinetic energy.Major part in steam S after stator blade 40 flows between the movable vane 50 of formation with one-level.The kinetic energy of steam S is converted to kinetic energy of rigid body by movable vane 50, and applies to rotate to axis body 30.On the other hand, the part (such as, several percentage points) in steam S flows in annular slot 111, becomes so-called leaked steam thus after flowing out from stator blade 40.
At this, as shown in Fig. 3 (a), first the steam S flowed in annular slot 111 flows into the first cavity C 1, collides with the ladder surface 53A of first order stepped part 52A.Steam S returns upstream side, produces the main whirlpool Y1 be such as rotated counterclockwise on the paper of Fig. 3 thus.
Now, especially at the rising wood 55A of first order stepped part 52A, a part of fluid is peeled off from main whirlpool Y1, and thus in the mode that edge and this main whirlpool Y1 opposite direction rotate, the mode in this example for turning clockwise on Fig. 3 paper is peeling whirlpool Y2.
At this, the ladder surface 53A of first order stepped part 52A forms rake 56A to roll oblique mode to downstream.Therefore, compared with the situation not forming rake 56A with ladder surface 53A, the velocity vector on the rising wood 55A of main whirlpool Y1 rolls tiltedly towards sealing fin 15A.Thus, compared with the situation not forming rake 56A with ladder surface 53A, the diameter of the stripping whirlpool Y2 that the upper surface 152A of first order stepped part 52A is formed diminishes.
Such stripping whirlpool Y2 plays the effect of the leak fluid reduced through the micro-gap H1 sealed fin 15A and stepped part 52A, i.e. contracted flow effect.
That is, as shown in Fig. 3 (a), when forming stripping whirlpool Y2, this stripping whirlpool Y2 forms the sinking of velocity vector towards radially inner side in the axial upstream side of sealing fin 15A front end.This sinking has towards the inertial force of radially inner side the immediately front of micro-gap H1, therefore plays the effect (contracted flow effect) that the fluid through micro-gap H1 is shunk to radially inner side.Thus, the leakage flow of steam S diminishes.
At this, as shown in Figure 3 (b), when supposing that peeling off whirlpool Y2 is formed as positive round, when peeling off the diameter of whirlpool Y2 and become the twice of micro-gap H1 and periphery contacting with sealing fin 15A, it is consistent with the front end (interior ora terminalis) sealing fin 15A that the velocity component F towards radially inner side in the sinking that this stripping whirlpool Y2 is formed reaches maximum position.In this case, sinking passes through the immediately front of micro-gap H1 at faster speed, therefore reaches maximum to the contracted flow effect of leak fluid.
In the present embodiment, rake 56A is formed at the ladder surface 53A of first order stepped part 52A.Therefore, with do not form the situation of rake 56A at ladder surface 53A compared with, the diameter peeling off whirlpool Y2 diminishes, therefore the easy twice diameter peeling off whirlpool Y2 being set as micro-gap H1.
In addition, by sealing fin 15A and when being L1 than the distance definition between rising wood 55A seal fin 15A and lean on the rake 56A of upstream side, as long as the tilt angle theta 1 of setpoint distance L1 and rake 56 and make the diameter of stripping whirlpool Y2 be the twice of micro-gap H1.
Then, flow into the second cavity C 2 by the steam S after micro-gap H1, collide with the ladder surface 53B of second level stepped part 52B.Steam S returns upstream side, produces the main whirlpool Y1 be such as rotated counterclockwise on the paper of Fig. 3 thus.And at the rising wood 55B of second level stepped part 52B, a part of fluid is peeled off from main whirlpool Y1, thus in the mode that edge and this main whirlpool Y1 opposite direction rotate, the mode in this example for turning clockwise on the paper of Fig. 3 is peeling whirlpool Y2.
And, flow into the 3rd cavity C 3 by the steam S after micro-gap H2, collide with the ladder surface 53C of third level stepped part 52C.Steam S returns upstream side, produces the main whirlpool Y1 be such as rotated counterclockwise on the paper of Fig. 3 thus.And at the rising wood 55C of third level stepped part 52C, a part of fluid is peeled off from main whirlpool Y1, thus in the mode that edge and this main whirlpool Y1 opposite direction rotate, the mode in this example for turning clockwise at the paper of Fig. 3 is peeling whirlpool Y2.
At this, more tend to downstream side, the density of steam S is less, therefore the cavity C in downstream side, and the flow velocity in the meridian plane of steam S is faster.Therefore, strong towards the flowing of radial outside with the steam S of ladder surface 53A collision rift in the first cavity C 1 towards the flowing ratio of radial outside with the steam S of ladder surface 53B collision rift in the second cavity C 2.Therefore, the diameter of the stripping whirlpool Y2 upper surface 152B of second level stepped part 52B formed easily is greater than the diameter of the stripping whirlpool Y2 formed on the upper surface 152A of first order stepped part 52A.
Equally, in the 3rd cavity C 3, the diameter of the stripping whirlpool Y2 that the upper surface 152C of third level stepped part 52C is formed easily is greater than the diameter of the stripping whirlpool Y2 formed on the stepped part 52B of the second level.
But, in the present embodiment, tilt angle theta 1 ~ the θ 3 of rake 56A ~ 56C that each ladder surface 53A ~ 53C is formed is set as meeting θ 3 > θ 2 > θ 1, namely more tends to downstream side larger (with reference to Fig. 2).Therefore, it is possible to make the velocity vector of the stripping whirlpool Y2 formed in each cavity C (C1 ~ C3) towards sealing fin 15(15A ~ 15C) side (axis).Therefore, each diameter peeling off whirlpool Y2 is roughly the same size.
In addition, the same with distance L1 and tilt angle theta 1, as long as set the sealing fin 15B corresponding with second level stepped part 52B and than seal fin 15B by the rake 56B of upstream side rising wood 55B between distance L2 and the tilt angle theta 2 of rake 56B, and make the diameter of stripping whirlpool Y2 be the twice of micro-gap H2.In addition, the same with distance L1 and tilt angle theta 1, as long as the sealing fin 15C of setting and third level stepped part 52C and than the distance L3 between rising wood 55C seal fin 15C and lean on the rake 56C of upstream side and the tilt angle theta 3 of rake 56C, and the diameter of stripping whirlpool Y2 is made to be the twice of micro-gap H3.
(effect)
Therefore, according to above-mentioned mode of execution, three stepped part 52(52A ~ 52C are formed) at blade tip guard shield 51, and be formed at the annular slot 111 of dividing plate foreign steamer 11 and stepped part 52(52A ~ 52C) corresponding position arranges three respectively and seals fin 15(15A ~ 15C), thus can at each sealing fin 15(15A ~ 15C) upstream side formed and peel off whirlpool Y2.This stripping whirlpool Y2 forms the sinking of velocity vector towards radially inner side in the axial upstream side of sealing fin 15A, reduces through each micro-gap H(H1 ~ H3 therefore, it is possible to play) the effect of leak fluid, i.e. contracted flow effect.
In addition, at stepped part 52(52A ~ 52C) ladder surface 53(53A ~ 53C) be formed with rake 56(56A ~ 56C), rake 56(56A ~ 56C) tilt angle theta 1 ~ θ 3 to be set as more tending to downstream side larger.That is, tilt angle theta 1 ~ θ 3 is set as meeting θ 3 > θ 2 > θ 1.
Therefore, the diameter of stripping whirlpool Y2 formed in each cavity C (C1 ~ C3) is roughly the same size, therefore, it is possible to make each sealing fin 15(15A ~ 15C) the sinking grow of axial upstream side.Reduce through each micro-gap H(H1 ~ H3 therefore, it is possible to reliably play) the effect of leak fluid, i.e. contracted flow effect.
In addition, in the above-described embodiment, following situation is illustrated: each ladder surface 53(53A ~ 53C) for being formed rake 56(56A ~ 56C by excising obliquely) state, rake 56(56A ~ 56C) rising wood 55(55A ~ 55C) for and stepped part 52(52A ~ 52C) upper surface 152(152A ~ 152C) state that is connected.But, be not limited thereto, with at least with stepped part 52(52A ~ 52C) upper surface 152(152A ~ 152C) mode that is connected excises each ladder surface 53(53A ~ 53C).
(the first variation)
More specifically be described based on Fig. 4 ~ Fig. 8.
Fig. 4 is the schematic configuration sectional view of the first variation of stepped part.In addition, in the mode identical with above-mentioned mode of execution, mark identical label and be described (also identical for following variation).
As shown in Figure 4, be formed at three stepped part 52(52A ~ 52C of blade tip guard shield 51) ladder surface 53(53A ~ 53C) on, be formed with flat chamfered section 156(156A ~ 156C at end edge portion (edge part) respectively).That is, each ladder surface 53(53A ~ 53C) upper surface 152(152A ~ 152C) side excised obliquely.And, chamfered section 156(156A ~ 156C) rising wood 155(155A ~ 155C) with this upper surface 152(152A ~ 152C) be connected.
In addition, with regard to chamfered section 156(156A ~ 156C) with regard to, relative to the tilt angle theta 1, ~ θ 3 of radial direction, be set as more tending to downstream side (right side in Fig. 4) larger.That is, the tilt angle theta 1' of the chamfered section 156A ladder surface 53A of first order stepped part 52A formed, the tilt angle theta 2' of chamfered section 156B that the ladder surface 53B of second level stepped part 52B is formed and the tilt angle theta 3' of chamfered section 156C formed on the ladder surface 53C of third level stepped part 52C are set as meeting
θ3'＞θ2'＞θ1'。
Therefore, the first above-mentioned variation plays the effect identical with aforesaid mode of execution.In addition, chamfered section 156(156A ~ 156C) with the rake 56(56A ~ 56C forming aforesaid mode of execution) situation compared with, each stepped part 52(52A ~ 52C) resection few.Therefore, it is possible to cut down finished cost.
(the second variation)
Fig. 5 is the schematic configuration sectional view of the second variation of stepped part.In addition, in figures in the following, be formed with three stepped part 52(52A ~ 52C at blade tip guard shield 51) content identical with above-mentioned mode of execution.And, each stepped part 52(52A ~ 52C) structure identical, therefore only illustrate a part of stepped part 52, omit the diagram of other stepped part 52.
As shown in Figure 5, the difference of above-mentioned mode of execution and the second variation is, each stepped part 52(52A ~ 52C at above-mentioned mode of execution) ladder surface 53(53A ~ 53C) on be only formed with rake 56(56A ~ 56C respectively), relative to this, in the second variation, the attachment portion of the rake 56B that the upper surface 152A and second level stepped part 52B of first order stepped part 52A are formed, and the attachment portion of the rake 56C that the upper surface 152B of second level stepped part 52B and third level stepped part 52C is formed, the arcus part 57B of radius r 1 is formed in the mode caved in towards downstream side (right side in Fig. 5), 57C.
By arcus part 57B, the upper surface 152A of first order stepped part 52A is connected smoothly with the rake 56B formed at second level stepped part 52B.In addition, by arcus part 57C, the upper surface 152B of second level stepped part 52B is connected smoothly with the rake 56C formed at third level stepped part 52C.
Therefore, according to the second variation, leaked steam can be guided to rake 57(57A ~ 57C reposefully), thus can reduce from each rake 57(57A ~ 57C) rising wood 55(55A ~ 55C) energy loss of main whirlpool Y1 that flows out.Consequently, the sinking of stripping whirlpool Y2 can be made to become large, therefore, it is possible to make stripping whirlpool Y2 play larger contracted flow effect.
(the 3rd variation)
Fig. 6 is the schematic configuration sectional view of the 3rd variation of stepped part.
As shown in Figure 6, the difference of above-mentioned mode of execution and the 3rd variation is, each stepped part 52(52A ~ 52C at above-mentioned mode of execution) ladder surface 53(53A ~ 53C) on be only formed with rake 56(56A ~ 56C respectively), relative to this, in the 3rd variation, replace rake 56(56A ~ 56C), the only arcus part 256(256A ~ 256C of forming radius r2).
Arcus part 256(256A ~ 256C) formed in the mode caved in towards downstream side (right side in Fig. 6).And, arcus part 256(256A ~ 256C) rising wood 255(255A ~ 255C) with stepped part 52(52A ~ 52C) upper surface 152(152A ~ 152C) be connected.At this, rising wood 255(255A ~ 255C) on arcus part 256(256A ~ 256C) tangent direction and radial direction between angle θ A to be set as more tending to downstream side larger.
Therefore, the 3rd variation plays the effect identical with aforesaid mode of execution.In addition, compared with aforesaid mode of execution, more leaked steam can be guided to arcus part 256(256A ~ 256C reposefully) rising wood 255(255A ~ 255C), therefore, it is possible to make the energy loss of main whirlpool Y1 diminish.Consequently, the sinking of stripping whirlpool Y2 can be made to become large further, therefore, it is possible to make stripping whirlpool Y2 play larger contracted flow effect.
(the 4th variation)
Fig. 7 is the schematic configuration sectional view of the 4th variation of stepped part.
As shown in Figure 7, the difference of aforesaid first variation and the 4th variation is, stepped part 52(52A in the first variation ~ 52C) ladder surface 53(53A ~ 53C) on, flat chamfered section 156(156A ~ 156C is formed with respectively) at end edge portion (edge part), relative to this, flat chamfered section 156(156A ~ 156C in the 4th variation) on, the rounded corner portion 356(356A ~ 356C of radius r 3 is formed in lower edge side).
By rounded corner portion 356(356A ~ 356C), ladder surface 53(53A ~ 53C) peaceful chamfered section 156(156A ~ 156C) connect smoothly.Therefore, with ladder surface 53(53A ~ 53C) the steam S of collision rift guided to flat chamfered section 156(156A ~ 156C reposefully).Consequently, can reliably prevent at flat chamfered section 156(156A ~ 156C) lower edge part peel off from main whirlpool Y1 and form little stripping whirlpool Y2'(with reference to the double dot dash line Fig. 7).Therefore, it is possible to reduce the energy loss of main whirlpool Y1, therefore, it is possible to make to become large based on the contracted flow effect peeling off whirlpool Y2.
(the 5th variation)
Fig. 8 is the schematic configuration sectional view of the 5th variation of stepped part.
As shown in Figure 8, the difference of aforesaid 3rd variation and the 5th variation is, each stepped part 52(52A ~ 52C in the 5th variation) ladder surface 53(53A ~ 53C) the arcus part 456(456A ~ 456C of radius r 4 that formed) and shape.
Namely, arcus part 256(256A ~ the 256C of the 3rd variation) formed in the mode caved in towards downstream side (right side in Fig. 6), in contrast, the arcus part 456(456A ~ 456C of the 5th variation) formed in the mode expanded towards upstream side (left side in Fig. 8).And, arcus part 456(456A ~ 456C) rising wood 455(455A ~ 455C) with stepped part 52(52A ~ 52C) upper surface 152(152A ~ 152C) be connected.
At this, rising wood 455(455A ~ 455C) on arcus part 456(456A ~ 456C) tangent direction and radial direction between angle θ B to be set as more tending to downstream side larger.
Therefore, the 5th above-mentioned variation plays the effect identical with aforesaid 3rd variation.
In addition, the present invention is not limited to above-mentioned mode of execution, without departing from the scope of spirit of the present invention, comprises the mode of execution after carrying out various change in the above-described embodiment.
Such as, in above-mentioned mode of execution or variation, using the dividing plate foreign steamer 11 established on the housing 10 as structure.But, be not limited thereto, dividing plate foreign steamer 11 also can not be set and using housing 10 itself as structure of the present invention.That is, this structure can be anyly specified the parts of stream by the mode between movable vane with fluid around movable vane 50.
In addition, in above-mentioned mode of execution or embodiment, describe following situation: the position corresponding with blade tip guard shield 51 at dividing plate foreign steamer 11 forms annular slot 111, by by ladder with three stepped part 52(52A ~ 52C) the recess 111A ~ 111C of expanding gradually three ring-types of corresponding mode and the diameter fourth stage recess 111D less than third level recess 111C formed this annular slot 111.But, be not limited thereto, also roughly the samely can diametrically form annular slot 111 overall.
And, in above-mentioned mode of execution or variation, describe following situation: multiple stepped part 52 is set at blade tip guard shield 51, also forms multiple cavity C thus.But be not limited thereto, the quantity of stepped part 52 and the cavity C corresponding with it is arbitrary, can be one, also can be more than three or four.
In addition, it is relative with a stepped part 52 that multiple sealing fin 15 also can be set.
In addition, in above-mentioned mode of execution or variation, the movable vane 50 and stator blade 40 of final level apply the present invention, but also can apply the present invention on the movable vane 50 of other grades and stator blade 40.
And, in above-mentioned mode of execution or variation, " blade " of the present invention is set to movable vane 50, forms stepped part 52(52A ~ 52C at the blade tip guard shield 51 of the front end as movable vane 50).In addition, " structure " of the present invention is set to dividing plate foreign steamer 11, dividing plate foreign steamer 11 arranges sealing fin 15(15A ~ 15C).But, be not limited thereto, also " blade " of the present invention can be set to stator blade 40, form stepped part 52 at the front end of stator blade 40.In addition, also " structure " of the present invention can be set to axis body (rotor) 30, axis body 30 arranges sealing fin 15.Also above-mentioned mode of execution or variation can be used for stepped part 52 in this case.
In addition, in the above-described embodiment, be the example of the steam turbine 1 applying the present invention to condensed steam type, but also can apply the present invention to the steam turbine in other patterns, such as secondary air exhausting type turbine, air exhausting type turbine, mixed-gas type turbine etc.
And, in the above-described embodiment, be the example applying the present invention to steam turbine 1, but also can apply the present invention to gas turbine, even can apply the present invention to all equipment with pivoting leaf.
Industrial applicibility
The present invention relates to a kind of turbine for such as power station, chemical plant, gas plant, iron works, boats and ships etc.According to the present invention, the leakage rate of working fluid can be reduced.
Label declaration
1 steam turbine (turbine)
10 housings
11 dividing plate foreign steamers (structure)
15(15A ~ 15C) seal fin
30 axis bodies (structure)
40 stator blades (blade)
41 wheel hub protective cap
50 movable vanes (blade)
51 blade tip guard shields
52(52A ~ 52C) stepped part
53(53A ~ 53C) ladder surface
55(55A ~ 55C), 155(155A ~ 155C), 455(455A ~ 455C) rising wood
56(56A ~ 56C) rake
57B, 57C, 256(256A ~ 256C), 456(456A ~ 456C) arcus part
156(156A ~ 156C) flat chamfered section (cut portion)
356(356A ~ 356C) rounded corner portion
C(C1 ~ C3) cavity
H(H1 ~ H3) micro-gap
K gap
S steam
The main whirlpool of Y1
Y2 peels off whirlpool
θ 1 ~ θ 3, θ 1' ~ θ 3' angle of inclination
θ A, θ B angle
Claims (2)
1. a turbine, possesses:
Blade;
Structure, leaves gap and is arranged at the front end side of described blade, and relatively rotating relative to described blade;
Stepped part, is arranged on any one party in the described front end of described blade and the described structure position relative with described front end, has ladder surface and give prominence to towards the opposing party;
Sealing fin, be arranged on any the opposing party in the described front end of described blade and the described structure position relative with described front end, extend towards described stepped part, and form micro-gap between this stepped part, fluid circulates in described gap; And
Cut portion, is formed at described ladder surface in the mode be connected with the upper surface of described stepped part, is guided in the stripping whirlpool that the main flow from described fluid is peeled off at the upper surface of described stepped part towards described sealing fin, wherein,
Described stepped part has multiple described ladder surface, and is formed in the mode that projecting height uprises from upstream side gradually towards downstream side,
Described cut portion is the rake being formed at each ladder surface and tilting towards described downstream side from described upstream side,
Each rake is set as that relative to the angle of inclination of running shaft radial direction the described angle of inclination of the described rake formed at the described ladder surface in described downstream side is larger.
2. a turbine, possesses:
Blade;
Structure, leaves gap and is arranged at the front end side of described blade, and relatively rotating relative to described blade;
Stepped part, is arranged on any one party in the described front end of described blade and the described structure position relative with described front end, has ladder surface and give prominence to towards the opposing party;
Sealing fin, be arranged on any the opposing party in the described front end of described blade and the described structure position relative with described front end, extend towards described stepped part, and form micro-gap between this stepped part, fluid circulates in described gap; And
Cut portion, is formed at described ladder surface in the mode be connected with the upper surface of described stepped part, is guided in the stripping whirlpool that the main flow from described fluid is peeled off at the upper surface of described stepped part towards described sealing fin, wherein,
Described stepped part has multiple described ladder surface, and is formed in the mode that projecting height uprises from upstream side gradually towards downstream side,
Described cut portion has arcus part, and this arcus part is formed at each ladder surface, and is connected with described upper surface smoothly from described upstream side towards described downstream side,
Angular setting between the tangent direction at the position that described arcus part is connected with described upper surface and running shaft radial direction is that the described angle of the described arcus part formed at the described ladder surface in described downstream side is larger.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010286583A JP5517910B2 (en) | 2010-12-22 | 2010-12-22 | Turbine and seal structure |
| JP2010-286583 | 2010-12-22 | ||
| PCT/JP2011/079808 WO2012086757A1 (en) | 2010-12-22 | 2011-12-22 | Turbine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103228871A CN103228871A (en) | 2013-07-31 |
| CN103228871B true CN103228871B (en) | 2015-07-15 |
Family
ID=46314024
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201180056739.9A Expired - Fee Related CN103228871B (en) | 2010-12-22 | 2011-12-22 | Turbine |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US9353640B2 (en) |
| EP (1) | EP2657452B1 (en) |
| JP (1) | JP5517910B2 (en) |
| KR (1) | KR101464910B1 (en) |
| CN (1) | CN103228871B (en) |
| WO (1) | WO2012086757A1 (en) |
Families Citing this family (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5558138B2 (en) * | 2010-02-25 | 2014-07-23 | 三菱重工業株式会社 | Turbine |
| JP5484990B2 (en) * | 2010-03-30 | 2014-05-07 | 三菱重工業株式会社 | Turbine |
| JP5518022B2 (en) * | 2011-09-20 | 2014-06-11 | 三菱重工業株式会社 | Turbine |
| JP5916458B2 (en) | 2012-03-23 | 2016-05-11 | 三菱日立パワーシステムズ株式会社 | Turbine |
| KR102136879B1 (en) * | 2013-04-16 | 2020-07-23 | 엘지전자 주식회사 | turbo fan and ceiling type air conditioner using thereof |
| JP6296649B2 (en) | 2014-03-04 | 2018-03-20 | 三菱日立パワーシステムズ株式会社 | Seal structure and rotating machine |
| JP6530918B2 (en) * | 2015-01-22 | 2019-06-12 | 三菱日立パワーシステムズ株式会社 | Turbine |
| JP6227572B2 (en) * | 2015-01-27 | 2017-11-08 | 三菱日立パワーシステムズ株式会社 | Turbine |
| JP6785041B2 (en) * | 2015-12-10 | 2020-11-18 | 三菱パワー株式会社 | Seal structure and turbine |
| JP2017145813A (en) | 2016-02-19 | 2017-08-24 | 三菱日立パワーシステムズ株式会社 | Rotary machine |
| FR3053386B1 (en) * | 2016-06-29 | 2020-03-20 | Safran Helicopter Engines | TURBINE WHEEL |
| JP2018003812A (en) * | 2016-07-08 | 2018-01-11 | 三菱日立パワーシステムズ株式会社 | Bucket and turbine using the same |
| FR3055353B1 (en) * | 2016-08-25 | 2018-09-21 | Safran Aircraft Engines | LABYRINTH SEAL ASSEMBLY FOR TURBOMACHINE COMPRISING ABRADABLE AND INCLINED LECHETTES |
| JP6706585B2 (en) * | 2017-02-23 | 2020-06-10 | 三菱重工業株式会社 | Axial rotating machine |
| JP6917162B2 (en) * | 2017-02-28 | 2021-08-11 | 三菱パワー株式会社 | Blades, rotor units, and rotating machines |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1001139A1 (en) * | 1998-11-10 | 2000-05-17 | Asea Brown Boveri AG | Turbine blade tip sealing |
| US6340284B1 (en) * | 1998-12-24 | 2002-01-22 | Alstom (Switzerland) Ltd | Turbine blade with actively cooled shroud-band element |
| CN2725533Y (en) * | 2004-07-28 | 2005-09-14 | 上海汽轮机有限公司 | High power steam turbine low pressure self crown carried long blade stepped surrounding belt |
Family Cites Families (29)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3897169A (en) * | 1973-04-19 | 1975-07-29 | Gen Electric | Leakage control structure |
| FR2374766A1 (en) | 1976-12-20 | 1978-07-13 | Lincoln Electric Co | Ignition circuit for IC engine driving self-excited generator - has field winding core with remanence insufficient for self-excitation when engine stops |
| JPS53104803U (en) * | 1977-01-31 | 1978-08-23 | ||
| FR2452601A1 (en) * | 1979-03-30 | 1980-10-24 | Snecma | REMOVABLE SEALING COVER FOR TURBOJET BLOWER HOUSING |
| JPS5951104A (en) | 1982-09-17 | 1984-03-24 | Hitachi Ltd | Internal structure of turbine stage |
| JPS6123804A (en) | 1984-07-10 | 1986-02-01 | Hitachi Ltd | Turbine stage structure |
| JPS61134501A (en) | 1984-12-06 | 1986-06-21 | 株式会社東芝 | Integral once-through type steam generator |
| JPS6361501A (en) | 1986-09-01 | 1988-03-17 | Matsushita Electric Ind Co Ltd | Plane antenna jointed with frequency converter into one body |
| GB2226365B (en) * | 1988-12-22 | 1993-03-10 | Rolls Royce Plc | Turbomachine clearance control |
| JPH0435601A (en) | 1990-05-31 | 1992-02-06 | Kunimitsu Masuda | Manufacture of ornamental body for accessory |
| JPH04350302A (en) | 1991-05-28 | 1992-12-04 | Hitachi Ltd | Stage structure of turbine |
| JPH0913905A (en) | 1995-06-30 | 1997-01-14 | Mitsubishi Heavy Ind Ltd | Turbine |
| JPH10311205A (en) * | 1997-05-14 | 1998-11-24 | Toshiba Corp | Axial flow turbine |
| DE59710621D1 (en) * | 1997-09-19 | 2003-09-25 | Alstom Switzerland Ltd | Gap sealing device |
| JPH11148307A (en) | 1997-11-17 | 1999-06-02 | Hitachi Ltd | Seal structure of turbine |
| JPH11200810A (en) | 1998-01-09 | 1999-07-27 | Mitsubishi Heavy Ind Ltd | Labyrinth seal mechanism |
| JP2002228014A (en) | 2001-02-05 | 2002-08-14 | Mitsubishi Heavy Ind Ltd | Labyrinth seal |
| JP2004332616A (en) | 2003-05-07 | 2004-11-25 | Toshiba Corp | Axial flow type turbomachine |
| JP2006291967A (en) | 2006-05-29 | 2006-10-26 | Toshiba Corp | Axial flow turbine |
| JP2009047043A (en) | 2007-08-17 | 2009-03-05 | Mitsubishi Heavy Ind Ltd | Axial flow turbine |
| US20090072487A1 (en) | 2007-09-18 | 2009-03-19 | Honeywell International, Inc. | Notched tooth labyrinth seals and methods of manufacture |
| JP2010216321A (en) * | 2009-03-16 | 2010-09-30 | Hitachi Ltd | Moving blade of steam turbine, and steam turbine using the same |
| DE102009040758A1 (en) * | 2009-09-10 | 2011-03-17 | Mtu Aero Engines Gmbh | Deflection device for a leakage current in a gas turbine and gas turbine |
| JP2011080452A (en) | 2009-10-09 | 2011-04-21 | Mitsubishi Heavy Ind Ltd | Turbine |
| DE102009052314A1 (en) * | 2009-11-07 | 2011-05-12 | Mtu Aero Engines Gmbh | Sealing arrangement for a gas turbine and such a gas turbine |
| US20110156359A1 (en) | 2009-12-31 | 2011-06-30 | General Electric Company | Turbine engine seals |
| JP5484990B2 (en) | 2010-03-30 | 2014-05-07 | 三菱重工業株式会社 | Turbine |
| EP2390466B1 (en) * | 2010-05-27 | 2018-04-25 | Ansaldo Energia IP UK Limited | A cooling arrangement for a gas turbine |
| JP5709447B2 (en) * | 2010-09-28 | 2015-04-30 | 三菱日立パワーシステムズ株式会社 | Turbine |
-
2010
- 2010-12-22 JP JP2010286583A patent/JP5517910B2/en active Active
-
2011
- 2011-12-22 WO PCT/JP2011/079808 patent/WO2012086757A1/en active Application Filing
- 2011-12-22 EP EP11851503.0A patent/EP2657452B1/en not_active Not-in-force
- 2011-12-22 CN CN201180056739.9A patent/CN103228871B/en not_active Expired - Fee Related
- 2011-12-22 US US13/995,542 patent/US9353640B2/en not_active Expired - Fee Related
- 2011-12-22 KR KR1020137013349A patent/KR101464910B1/en active IP Right Grant
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1001139A1 (en) * | 1998-11-10 | 2000-05-17 | Asea Brown Boveri AG | Turbine blade tip sealing |
| US6340284B1 (en) * | 1998-12-24 | 2002-01-22 | Alstom (Switzerland) Ltd | Turbine blade with actively cooled shroud-band element |
| CN2725533Y (en) * | 2004-07-28 | 2005-09-14 | 上海汽轮机有限公司 | High power steam turbine low pressure self crown carried long blade stepped surrounding belt |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2657452A4 (en) | 2014-06-11 |
| JP2012132397A (en) | 2012-07-12 |
| US20130272855A1 (en) | 2013-10-17 |
| WO2012086757A1 (en) | 2012-06-28 |
| EP2657452B1 (en) | 2019-05-22 |
| JP5517910B2 (en) | 2014-06-11 |
| US9353640B2 (en) | 2016-05-31 |
| CN103228871A (en) | 2013-07-31 |
| KR20130114165A (en) | 2013-10-16 |
| EP2657452A1 (en) | 2013-10-30 |
| KR101464910B1 (en) | 2014-11-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103228871B (en) | Turbine | |
| CN102449268B (en) | Turbine | |
| CN102834589B (en) | Turbine | |
| EP2623722B1 (en) | Turbine with blades having a tip shroud | |
| CN104024581B (en) | Turbine | |
| EP2617942B1 (en) | Turbine with shrouded blades | |
| JP5725848B2 (en) | Turbine | |
| CN104204419B (en) | Turbine | |
| CN102695849A (en) | Turbine | |
| CN105074134A (en) | Rotating machine | |
| CN111287801B (en) | Steam turbine | |
| CN103717842A (en) | Turbine | |
| EP3012409B1 (en) | Turbine assembly | |
| CN107109943A (en) | Turbine moving blade and variable capacity turbine | |
| CN104736906A (en) | Rotating machine | |
| KR102290579B1 (en) | rotor blades, rotor units and rotary machines | |
| JPH11173104A (en) | Turbine rotor blade | |
| JP2013100820A (en) | Turbine | |
| JP2020139464A (en) | Axial flow turbine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| ASS | Succession or assignment of patent right |
Owner name: MITSUBISHI HITACHI POWER SYSTEM LTD. Free format text: FORMER OWNER: MITSUBISHI JUKOGIO KK Effective date: 20150302 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20150302 Address after: Kanagawa Applicant after: MITSUBISHI HEAVY INDUSTRIES, Ltd. Address before: Tokyo, Japan Applicant before: MITSUBISHI HEAVY INDUSTRIES, Ltd. |
|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CP01 | Change in the name or title of a patent holder | ||
| CP01 | Change in the name or title of a patent holder |
Address after: Kanagawa Prefecture, Japan Patentee after: Mitsubishi Power Co.,Ltd. Address before: Kanagawa Prefecture, Japan Patentee before: MITSUBISHI HEAVY INDUSTRIES, Ltd. |
|
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20150715 Termination date: 20211222 |